SU1721333A1 - Dog safety coupling - Google Patents

Abstract

The invention relates to mechanical engineering and can be used to protect high-speed machines from overloads. The purpose of the invention is to reduce labor costs for the manufacture and lining of the coupling. The clutch consists of a master 1 and a slave 2 half couplings (P) with cams (K) at the ends. Radial 21 are mounted on the leading П 1 and shown in Fig. 1A, on which centrifugal weights 17 are mounted. Between P there is a ring 5 with K at the ends preloaded by a spring 15. P 1 is mounted on the shaft 8 with the possibility of axial displacement and fixation of its position a nut 10 and a lock nut 11. When the shaft rotates, torque on П 2 is transmitted by engaging To intermediate ring P 1 and 2. When the calculated torque K increases, ring 5 is pressed from K half-coupling 2 and ring 5 moves in axial direction, compressing spring 15. When To get out of the mesh, center the beacon weights 17 move and hold the ring 5, breaking the contact of the ring and the P 2. After the rotational frequency decreases, the centrifugal weights release the ring. For the run-in of spring 15, the distance between ring 5 and A 1 is changed so that ring 5 does not fixate. This allows multiple closure and opening of K to occur without additional operations, which reduces labor costs for adjusting the coupling. 1 hp f-ly, 7 ill. 5 years (L C N Yu ha / b, p and CO CJ C 18

Description

The invention relates to mechanical engineering and can be used in all sectors of the national economy to protect high-speed machines and mechanisms from overloads.

The aim of the invention is to reduce labor costs for the manufacture and debugging of the clutch by adjusting the position of the drive coupling half.

FIG. 1 shows the coupling, axial section; in fig. 2 is a diagram of the forces acting on the intermediate ring element in the transmission of torque; in fig. 3 shows section A-A in FIG. one; in fig. 4 shows the mutual arrangement of the weights and the intermediate ring element in the process of opening; in fig. 5 shows the relative position of the cams of the coupling halves and the intermediate element in the process of opening the coupling; in fig. 6 shows the mutual arrangement of the centrifugal weights and the intermediate ring element when the coupling is fully opened; in fig. 7 shows the relative position of the cams of the coupling halves and the intermediate ring element when the clutch is fully opened.

The cam clutch contains a leading 1 and a driven 2 half coupling with cams 3 and 4 on the end surfaces facing one another, an intermediate ring element 5 with cams 6 and 7 on both ends contacting with the cams 3 and 4 half coupling 1 and 2. On the leading shaft 8 by means of splines or key 9 is installed leading half coupling 1, fixed from axial movements by a nut 10 mounted on shaft 8, and a cap lock nut 11 mounted on half of the coupling half 1.

The coupling half 2 is mounted on the shaft 8 on rolling or sliding bearings 12 and fixed from the axial displacement by a crown nut 13. The forces acting on its cams 4 and the elements 14 connecting the coupling with the actuator prevent the left coupling half 2 from moving. . The axial fixation of the driven half coupling 2 on the shaft 8 can also be carried out with the help of other details, for example with the help of locking rings. The intermediate ring element 5 is installed between the coupling halves 1 and 2 on the shaft 8 with a gap and is spring-loaded relative to the driven coupling half 2 by means of a calibrated spring 15. The adjacent cams 3 and b of the driving coupling half 1 and the intermediate element 5 are larger in height than the adjacent cams 4 and 7 driven the coupling half 2 and intermediate element 5, and the angle profile of adjacent cams 3 and 6 is smaller than the angle profile of adjacent cams 4 and 7. The outer diameter of adjacent cams 3 and 6 can be larger or smaller than the outer diameter of adjacent cams 4 and 7.

The engagement of the cams of the coupling halves is made so that during overloads the intermediate ring member 5 has the possibility of axial movement. On the cams 3 of the leading half coupling 1 radially

guides 16 are fixed on which centrifugal weights 17 of arcuate shape having a conical surface are mounted with a possibility of movement. The rotation of the load 17 around the axis of the guides

16 prevents the inner end of the leading coupling half 1. The guides and weights are mounted on the cams 3 of the leading coupling half

1 so that in the closed position of the half coupling the distance between the vertices of the conical

the surfaces of the weights 1.7 and the annular groove 18 on the inner surface of the intermediate ring element 5 are smaller than the height of the cams in the engagement of the intermediate element 5 and the driven coupling half 2.

The clutch is closed by a collection housing 19. which is attached to the driven half coupling 2 with screws 20. The sealing is performed by the cuff 21 and the ring 22. At the end of the driven coupling half 2, a hole is made closed by the stopper 23 with sealing 24. serving to fill and control the oil level in the housing. To eliminate imbalance, if necessary, at the end of the same coupling half

Balancing weights may be installed at the appropriate places.

The clutch is preliminarily adjusted to transmit the required torque, for which a spring 15 is selected, which presses the intermediate ring element 5 to the driven coupling half 2. The required force of the spring 15 is determined from the relation

Pnp-2L tfl (z .- /.) -F tg (y- / o) - Rff,

where T is the torque transmitted by the clutch, Nm;

D is the outer diameter of adjacent cams 4 and 7 of the driven coupling half 2 and the intermediate ring element 5, m;

d is the outer diameter of adjacent cams 3 and 6 of the leading coupling half 1 and the intermediate ring element 5, m;

a is the angle of the cam profile of the engagement of the intermediate ring element 5 and the driven half-coupling 2, degrees;

y-angle of the cams of engagement of the leading coupling half 1 and the intermediate ring element 5, degrees;

p - friction angle on cam surfaces, hail;

Rc - centrifugal force of cargo 17, N;

f - coefficient of friction of goods 17 about intermediate element 5.

In order to increase the accuracy and stability of the operation, after the installation of the required spring, the run-in is performed, for which the leading coupling half 1 together with the centrifugal weights 17c using the nut 10 and the locking lock nut 11 is mounted on the shaft 8 so that when the clutch opens, the centrifugal weights 17 do not enter an annular groove 18 on the intermediate annular element 5. The required position of the leading coupling half 1 on the shaft 8 is ensured by observing the previously known size A1 (Fig. 1). During the run-in, the intermediate ring element 5 is not fixed by the weights in the open position, which ensures a smooth re-closure of the coupling. The opening and closing cycles (5000-6000) are repeated during the whole burn-in time. After running in the coupling, the coupling half 1 together with the centrifugal weights 17 is mounted on the shaft 8 with the nut 10 and the lock nut 11 on the shaft 8 so that the distance between the tops of the tapered surfaces of the loads 17 and the ring groove on the intermediate element 5 is less than the height of the adjacent cams of the driven half coupling 2 and the element 5. This position of the leading coupling half is also ensured by observing the predetermined size A (Fig. 1).

The torque from the drive shaft 8 is transmitted to the leading coupling half 1, and from it through the cams to the intermediate element 5 and then through the cams to the driven coupling half 2 rigidly connected to the flange 14 or to any other element connecting the coupling half 2 with a secured drive . At the same time, the weights 17 are centrifugally pressed against the inner surface of the intermediate ring element 5.

When the resistance moment on the driven half coupling changes, the axial force acting in the engagement of the cams of the driving half coupling 1 and intermediate element 5 and the pressing intermediate element 5 against the driven coupling half 2 changes. Thus, with an increase in the resistance moment on the driven coupling half 2, this force also increases. But since the profile angle of adjacent cams 7 and 4 of the intermediate element 5 and the driven coupling half 2 is greater than the profile angle of the adjacent cams 3 and 6 of the driving coupling half 1 and the intermediate element 5, the repulsive force of the coupling half A and element 5 increases as the resistance moment increases. At the moment when the repulsive force of the half-coupling 2 and the element 5 equilibrates the axial force acting in the engagement of the leading coupling half 1 and the intermediate element 5, and the force of the spring 15, the coupling opens, i.e. intermediate element 5 moving along

10, shaft 8, is disengaged from the driven half coupling 2. In the closed position of the coupling, the intermediate element 5 is centered over the cams in engagement with the driving 1 and driven by the 2 coupling halves, as well as with the centrifugal forces of the weights 17 and the spring force 15.

At the final stage of the output of the cams of the intermediate element 5 from engagement with the cams of the driven half-coupling 2 into contact

0, with the conical surface of the annular groove 18 on the inner surface of the intermediate element 5, enters the conical surface of the weights 17 (Figs. 4 and 5), which are displaced under the action of centrifugal forces

5 by guides 16 in the radial direction, and the resulting axial forces, compressing the spring 15, withdrawing the cams 7 of the intermediate element 5 from engagement with the cams 4 of the driven half-coupling 2 and retracting

0 intermediate element 5 from driven half coupling 2 for a given distance. The transmission of torque to the driven half coupling stops, the Intermediate element is centered on the cams of the leading half coupling 1, as well as by the centrifugal forces of the loads 17 and the spring force 15. The intermediate element 5 is held by the loads 17 in the open position (Fig. 6 and 7) as long as transmitted

0 rotation on the drive shaft 8. In this case, it is necessary that the condition

RC Pnp (tg / + Tpriv),

5 where Рц is the centrifugal force of the loads 17, Н; Rpr spring force 15..H; (5 - the angle of inclination of the forming conical surfaces of the weights 17 and the annular groove on the intermediate element 5 to the base, deg;

fnpne reduced coefficient of friction of the goods 17 on the guide 16 and the intermediate element 5.

When the shaft 8 is stopped, the centrifugal force of the weights 17 decreases from its maximum value to zero. At a certain value of the frequency of rotation of the shaft 8, the intermediate element 5, acting on the tapered surface of the annular groove on the tapered surface of the weights 17, begins to move them to their original position. When the cargo leaves the annular groove, the coupling closes. To close the clutch it is necessary that the condition

FU Pnp (tg p-tpriv) "

At the moment of launch, when large angular accelerations act, an inertia force additionally arises in the engagement of the cams of the master half coupling and intermediate member, which presses intermediate member 5 against the driven half coupling 2, which allows the clutch to transmit, without transferring the nominal torque, without opening , starting load.

When braking the driven half coupling, when negative accelerations act, this inertia force contributes to the opening of the coupling.

The clutch allows for additional burn-in without additional elements and full development, which reduces the labor costs for debugging the clutch.

Claims (2)

1.Kulachkova safety clutch containing the drive and the driven coupling mounted on the connected shafts with cams on mutually reversed ends, axially interposed between said ends, an intermediate element in the form of a ring with cams on both ends in contact with the cams of the respective coupling halves, and the coupling locking mechanism in the open position, made in the form of arcuate centrifugal weights, installed in radial guides, made in the leading half coupling, characterized in that, in order to reduce labor costs for the manufacture and adjustment of the coupling, the leading coupling half is mounted on the shaft with the possibility of fixed axial movement relative to the driven half coupling and intermediate element. 2. Mufta pop. 1, characterized in that the means for fixing the axial position of the leading coupling half are made in the form mounted on the shaft and contacting with its end face with the end of the coupling half of the nut and the union lock nut installed on the half of the coupling half and the contacting inner end surface with the surface of the said nut facing it. FIG. 2 FIG. four 7 Phage. five / DHS FIG. 6 i b c FIG. 7 f & f $ five 2 -., r-